JP2008008154A - Double suction centrifugal pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double suction centrifugal pump with a good performance not only providing a stable head-capacity curve diagonally right down but also more improving the efficiency of an impeller to largely contribute to reduction of energy consumption. <P>SOLUTION: The invention is characterized in that the double suction centrifugal pump has a pump casing and the impeller rotatably equipped in the pump casing and the impeller has a central main plate, a plurality of symmetrically-shaped blades arranged back to back on opposite surfaces of the main plate and an outer plate provided at ends of the blades which are opposite from the central main plate, wherein the blades are inclined so that the ends on an outer plate side are situated before the ends on a central main plate side in a direction of rotation of the impeller. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a centrifugal pump, and more particularly to an improvement of an impeller of a double-suction centrifugal pump using two impellers and an impeller in which symmetrical blades are combined back to back.

In a centrifugal pump that mainly boosts a fluid by applying centrifugal force generated by rotation of an impeller to the fluid, a double suction centrifugal pump that combines two blades back to back and transports the fluid by one discharge volute is known. In this case, the blades of the impeller have a shape in which symmetrical ones as shown in Non-Patent Document 1 are combined back to back.

Turbo pump Association of turbo machinery p168 Figure 11.9

  A conventionally proposed double suction centrifugal pump will be described.

  Both the suction centrifugal pumps are roughly constituted by a pump casing composed of a suction casing part and a discharge casing part, and an impeller in which symmetrically shaped blades are combined back to back.

  When the impeller rotates together with the rotating shaft, the fluid moves in both suction centrifugal pumps, and the swirl flow of the suction casing portion brings the swirling flow to the suction opening of the impeller.

  After the fluid flows into the impeller, centrifugal force is applied to the fluid by the rotation of the impeller, and after the pressure is increased, the fluid that flows out from the discharge port of the impeller is collected together by the discharge casing part. It goes out of the suction centrifugal pump.

  In this type of suction pump, the reverse flow generated on the inlet side swirls in the vicinity of the inlet without being particularly suppressed by the spiral shape of the suction casing in the low flow rate region near the deadline.

  The swirling recirculation flow causes the flow having an increased angular momentum near the inlet of the impeller to flow into the impeller, so that the total lift is lowered. As a result, there was a strong tendency that the performance curve of the flow-total head did not become a stable curve with a lower right, and the total head was lowered near the deadline, resulting in a mountainous curve.

  In this case, for example, the intersection with the system curve is not determined when the pump is started, and the operation becomes unstable. In the worst case, the specified flow rate does not come out even if the valve is opened as it is. There were many.

  The object of the present invention is not only to solve the above-mentioned problems and provide a stable heading curve with a lower right side, but also to improve the efficiency of the impeller further and greatly contribute to the reduction of energy consumption. It is to provide a suction centrifugal pump.

  In order to solve the above-mentioned object, the present invention has a pump casing and an impeller rotatably provided in the pump casing, and a plurality of the impellers are arranged back-to-back on both sides of the central main plate and the main plate. A suction vortex pump having a symmetrically shaped wing and an outer plate provided at an end of the wing opposite to the main plate, wherein the wing has an end on the outer plate side on the end of the central main plate side. It is in the double suction centrifugal pump that is inclined so as to be positioned forward of the impeller in the rotational direction of the impeller.

  More specifically, in the double suction centrifugal pump having the above-described configuration, the central main plate has an outer diameter smaller than that of the outer plate, and adjacent wings arranged back to back on both surfaces of the main plate are outer peripheral edges of the central main plate. The further front side is characterized in that it is joined directly without the central main plate.

  More specifically, in the double suction centrifugal pump configured as described above, one blade and the other blade sandwiching the main plate are shifted in the rotation direction of the impeller.

  According to the present invention, it is possible to provide a high-performance double-suction centrifugal pump that can obtain a stable flow rate-total head curve that decreases to the right and that has improved the pump efficiency more than before.

  Embodiments of the present invention will be described with reference to the drawings.

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 and 3 to 5.

  As shown in FIGS. 1 and 3 to 5, both suction centrifugal pumps have an impeller 30, a pump casing 100 in which the impeller 30 is rotatably installed, and a rotating shaft 20 that fixes the impeller 30.

  As shown in FIGS. 1, 3, and 4, the impeller 30 is on the opposite side of the central main plate 200, a plurality of symmetrically shaped wings 210 arranged back to back on both sides of the central main plate 200, and the central main plate 200. An outer plate 220 is provided at the end of the wing 210. The blades 210 are curved so that the outer peripheral side is behind the impeller 30 in the rotational direction.

  As shown in FIGS. 3 and 4, the pump casing 100 includes a discharge casing portion 230 that encloses the outer peripheral discharge side of the impeller 30, and two suction ports 240 provided on both sides near the center of the impeller 30, Two suction casing portions 260 and 270 corresponding to 250 are provided. The two suction casing parts 260 and 270 have a spiral shape.

  The mechanical seals 280 and 290 are provided at sliding portions between the two suction ports 240 and 250 of the impeller 30 and the two suction casing portions 260 and 270. Due to the mechanical seals 280 and 290, the impeller 3 can suppress fluid leakage from the discharge casing portion 230 side to the suction casing portions 260 and 270.

  As shown in FIG. 3B, the blades 210 of the impeller 30 are inclined so that the end portion on the outer plate 22 side is located in front of the end portion on the central main plate 200 side in the rotation direction of the impeller 30. ing.

  The inclination angle is about 5 ° to 15 °. The angle of inclination is large on the center side of the impeller 3 and small on the outer peripheral side. The central side is about 10 ° to 15 °, and the outer peripheral side is about 5 ° to 10 °.

  The operation related to the inclination of the blade 210 will be described.

  It demonstrates from the flow inside the impeller of both suction vortex pumps.

  Generally, the blade shape used for both suction centrifugal pumps is a centrifugal impeller, and its internal flow is very complicated as shown in Non-Patent Document 1 “Turbomachine” P35.

  An outline of the mechanism of loss caused by the internal flow of the impeller is one of the major factors. The existence of the secondary flow, which is the in-plane velocity in the cross-sectional direction of the impeller flow path, is the size of the loss, that is, the flow of the impeller. It is greatly related to the occurrence of non-uniform flow in the linear direction.

  FIG. 2A is a diagram showing the shape of an impeller of a conventional double suction centrifugal pump as viewed from the axial direction, and FIG. 2B is a schematic diagram showing the flow direction in the vicinity of the blades of the conventional impeller.

  The main flow inside the impeller can be changed from the axial direction to the radial direction along the meridional shape from the suction port of the blade to the discharge port of the blade. At this time, the centrifugal force caused by the main flow and the pressure drop generated from the central main plate side to the outer plate side as seen on the meridian plane are balanced, but the centrifugal force is generated in the part of the boundary layer where the flow velocity is low near the blade surface. small.

  For this reason, it cannot flow against the pressure gradient and flows from the central main plate side toward the outer plate side as shown in FIG. 2B.

  Furthermore, the slow flow in the boundary layer that flows near the outer plate in the inter-blade flow path cannot counter the pressure gradient between the blade pressure surface and the suction surface caused by the Coriolis force of the mainstream flowing along the blade surface. In addition, it flows in the vicinity of the outer plate from the blade pressure surface toward the suction surface.

  Therefore, as shown in FIG. 2B, the slow flow in the main flow direction is eventually accumulated on the blade suction surface and the outer plate side near the exit of the impeller, and the speed difference in the main flow direction between this and other portions. Will increase and this will cause loss due to mixing at the blade exit.

  Therefore, in order to suppress the main flow direction speed difference and reduce the loss, it is necessary to control the secondary flow in the blade channel cross section as described above.

  On the other hand, in the first embodiment of the present invention, the impeller 30 is on the opposite side of the central main plate 200, the symmetrically shaped wings 210 that are arranged back to back on both sides of the central main plate, and the central main plate 200. In the double suction centrifugal pump having the outer plate 220 provided at the end of the blade 210, the blade 210 is arranged such that the end of the outer plate 220 is positioned forward of the impeller 30 in the rotation direction with respect to the end of the central main plate 200. Tilted.

  By adopting such a shape, the outer plate side of the blade is always positioned in front of the rotation direction and rotates from the suction port to the discharge port of the blade 210. For this reason, as shown in FIG. 3B, the boundary layer flow in the vicinity of the wing 210 is generated from the outer plate 220 toward the central main plate 200, and is generated from the central main plate 200 to the outer plate 220 described above. Counters the pressure gradient.

  Accordingly, the flow in the vicinity of the wing 210 viewed from the meridian plane is different from the conventional blade shown in FIG. 2B (B), and flows in the direction of the exit of the wing 210 as shown in FIG.

  By improving the flow, the accumulation of slow flow in the boundary layer near the blade 210 surface near the discharge port of the blade 210 is weakened, and the nonuniformity of the velocity in the main flow direction that increases the loss near the discharge port of the blade 210 is suppressed. As a result, the impeller efficiency is improved.

  Accordingly, the pump efficiency is improved, and an excellent double suction centrifugal pump with reduced energy consumption can be obtained.

  The contents described above relate to the flow near the design point of the pump. Next, the state of the flow in the low flow rate region near the pump cutoff will be described.

  In the vicinity of the deadline, as shown in FIG. 4A, in the conventional impeller, recirculation flows are generated at the suction port and the discharge port, respectively, and the main flow inside the impeller is greatly bent.

  In particular, in the case of both suction centrifugal pumps, a spiral type is applied to the suction casing, so that a large swirl is given to the flow flowing into the impeller by the recirculation flow on the suction port side rotating with the rotation of the impeller. . The angular momentum on the suction side increases, and the total lift is lowered in the low flow rate region. As a result, the total lift curve becomes a mountain-shaped characteristic.

  In contrast, in the first embodiment of the present invention, the outer plate 220 side of the blade 210 is always positioned forward in the rotation direction from the suction port of the blade 210 to the discharge port, so that the discharge port is recirculated. The flow changes.

  That is, the recirculation flow in the vicinity of the outlet is a region where the relative speed of the blade flow path is low, and the circumferential speed increases and the pressure is increased by the centrifugal force. After exiting, the air flows into the impeller 30 again.

  When this flow is the first embodiment of the present invention, as described above, the flow in the low-speed boundary layer flows from the outer plate 220 toward the central main plate 200, so that the region where the relative velocity is low is enlarged. As shown in FIG. 4 (b), the recirculation flow region becomes larger than that of the conventional impeller.

  Therefore, because of this reverse flow region, the outflow angle near the discharge port of the blade 210 becomes very large, increasing the total head of the low flow region near the deadline.

  As a result, as shown in FIG. 5, a stable right-falling total head curve from the deadline to the large flow rate range can be obtained, and stable pump operation can be achieved over the entire operating flow rate range.

  FIG. 6 shows a cross section of the impeller 30 of the double suction centrifugal pump according to the second embodiment of the present invention.

  Also in this embodiment, the line of intersection with the outer plate 220 of the impeller 30 (the intersection of the outer plate and the blades) is positioned forward in the rotational direction with respect to the line of intersection of the central main plate 200 and the blades 210 when viewed from the pump rotation axis direction. This is the same as in the first embodiment. The feature point is that the central main plate 200 does not exist in the vicinity of the discharge port of the blades 210, and the two blades 210 having symmetrical shapes combined back to back are connected to each other.

  That is, the central main plate 200 has an outer diameter smaller than that of the outer plate 220, and the adjacent wings 210 arranged back-to-back on both sides of the central main plate 200 are located on the front side of the outer peripheral edge of the central main plate 200 via the central main plate 200. Connect directly.

  In this way, the effects shown in the first embodiment can be obtained, and the center main plate 200 is not present on the outer peripheral side, so that friction loss can be reduced, and further high pump efficiency and low energy consumption can be achieved. A vortex pump can be obtained.

  FIG. 7 shows a cross section of an impeller of a double suction centrifugal pump according to the third embodiment of the present invention.

  Also in this embodiment, the line of intersection with the outer plate 220 of the impeller 30 is located forward of the rotation direction with respect to the line of intersection of the central main plate 200 and the blades 210 when viewed from the pump rotation axis direction. Absent. A feature point is that a large number of blades 210 formed on both surfaces of the central main plate 200 are provided at an equal pitch in the rotation direction of the impeller 30, and the blades 210 arranged on one side of the central main plate 200 and the blades 210 arranged on the other side in the rotation direction. Misaligned and back to back.

  In addition, the rotational position shifts at an intermediate point between the blades 210 arranged on the opposite side of the central main plate 200.

  In this way, the effects shown in the first embodiment can be obtained and, of course, fluctuations in the rotational pressure generated in the flow path from the blade 210 to the blade 210 of the impeller 30 are caused by the blade 210 to the blade 210. They are offset from each other by being offset in the direction of rotation by half the distance up to.

  For this reason, the pressure fluctuation in the discharge port of an impeller can be made small as a whole impeller, and the double suction centrifugal pump which suppressed vibration and noise can be obtained.

They are the axial direction sectional drawing (b) of the impeller concerning the 1st example of the present invention, and the figure (I) which looked at the impeller from the perimeter side. It is sectional drawing (B) which shows the state of the impeller shape of the both suction centrifugal pump of a prior art, and the state of an internal flow, and the figure (I) which looked at the impeller from the outer peripheral side. They are the axial sectional view (b) of the impeller of the both suction centrifugal pumps of the prior art, and the view (b) of the impeller viewed from the outer peripheral side. It is an axial sectional view (A) of the both suction centrifugal pump concerning the 1st example of the present invention, and a figure (B) showing a situation of a flow inside an impeller. It is two examples of sectional drawing (a) and (b) which shows the mode of the flow inside the impeller of the both suction vortex pump concerning the 1st example of the present invention. It is a figure which shows the effect concerning the 1st Example of this invention. It is sectional drawing (B) of the both suction vortex pump concerning the 2nd Example of this invention, and the figure (B) which shows the mode of the flow inside an impeller. It is sectional drawing (B) of the both suction vortex pump concerning the 3rd Example of this invention, and the figure (B) which shows the mode of the flow inside an impeller.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 100 ... Pump casing, 30 ... Impeller, 200 ... Central main board, 210 ... Wing, 220 ... Outer board.

Claims (9)

A pump casing and an impeller provided rotatably in the pump casing;
The impeller includes a central main plate, a plurality of symmetrically arranged wings arranged back-to-back on both sides of the central main plate, and a double suction vortex having an outer plate provided at an end portion of the wing opposite to the central main plate. In the pump,
The blade is inclined at least on the outer peripheral side of the impeller so that the end on the outer plate side is positioned forward of the end of the impeller in the rotation direction with respect to the end on the central main plate side. Double suction centrifugal pump. The double suction centrifugal pump according to claim 1,
The central main plate has a smaller outer diameter than the outer plate,
A double-suction centrifugal pump characterized in that adjacent wings arranged back-to-back on both surfaces of the main plate are directly joined to each other on the front side of the outer peripheral edge of the central main plate without going through the central main plate. The double suction centrifugal pump according to claim 1,
One suction blade and the other blade sandwiching the main plate are misaligned in the rotational direction of the impeller. In the both suction centrifugal pump according to claim 3,
The blades are provided at an equal pitch in the rotational direction of the impeller,
The double suction centrifugal pump characterized in that the displacement position of the blade in the rotational direction comes to an intermediate point between the blades arranged on the opposite side of the main plate. The double suction centrifugal pump according to claim 1,
The double suction pump according to claim 1, wherein the blade has a curved shape in which an outer peripheral side is rearward in the rotation direction of the impeller. In the double suction centrifugal pump according to claim 1 or 5,
The double suction centrifugal pump characterized in that the inclination is an inclination of about 5 ° to 15 °. In the double suction centrifugal pump according to claim 1 or 5,
The double suction centrifugal pump characterized in that the angle of inclination is large on the center side of the impeller and small on the outer peripheral side. In the double suction centrifugal pump according to claim 7,
The double suction centrifugal pump characterized in that the inclination angle is about 10 ° to 15 ° on the center side of the impeller and about 5 ° to 10 ° on the outer peripheral side. The double suction centrifugal pump according to claim 1,
The pump casing has a discharge casing portion surrounding the outer peripheral discharge side of the impeller, and two suction casing portions corresponding to two suction ports provided on both sides near the center of the impeller,
The two suction centrifugal pumps characterized in that the two suction casing parts have a spiral shape.

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